JP6877584B2 - Torque transmitter - Google Patents

Description

The present invention relates to the torque transmission device according to claims 1 and 4.

International Publication No. 2009/067987 is known to have a force transmission device for transmitting output between a driving machine and a driven portion, which is provided with a series damper.

An object of the present invention is to provide an improved torque transmission device.

The above problem is solved by the torque transmission device according to claims 1 and 4. Advantageous embodiments are described in the dependent claims.

The improved torque transmission device is a series damper having a first damper unit, a second damper unit, and a coupling unit, in which the torque transmission device can be rotatably supported around the axis of rotation. The first damper unit has a damper output side, the second damper unit has a damper input side, and the coupling unit is arranged between the damper output side and the damper input side. The coupling unit has a first coupling portion and a second coupling portion, and the first coupling portion and the second coupling portion are displaced from each other in the axial direction. By arranging, the first coupling portion couples the damper output side to the second coupling portion, and the second coupling portion couples the first coupling portion to the damper input side. , Turned out to be available.

As a result, the torque transmission device can be made into a modular structure, so that a part of the components of the torque transmission device can be changed according to the required characteristics of the torque transmission device, and this change can be changed to the changed component. It can be done without adapting the structural configuration of other components to. This fit is done by a two-part coupling unit.

In another embodiment, the torque transmitter comprises a driven shaft, the coupling unit has a coupling hub, the coupling hub is rotatably supported by the driven shaft, and the coupling hub is on the peripheral surface. It has an external dentition, the first coupling has an internal dentition, the second coupling has another internal dentition, an internal dentition and another internal dentition. Engage within the external dentition. This makes it possible to provide axial tolerance compensation between the first damper unit and the second damper unit. Further, since the coupling portion can be inserted in the axial direction during the assembly of the torque transmission device, the assembly time is particularly short, and the assembly can be performed automatically.

In another embodiment, the torque transfer device comprises a tensioning means, which is between the first component and the second component, preferably the first coupling portion and the second cup. Arranged between the ring and the tensioning means, the tensioning means is such that the first component is relative to the second component, preferably the first coupling is relative to the second coupling. , Axial and / or circumferentially tensioned. As a result, tolerance compensation in the circumferential direction can be achieved.

The improved torque transmission device allows the torque transmission device to be rotatably supported around the axis of rotation, and the torque transmission device includes a turbine wheel of a hydrodynamic converter and a series damper, and a series damper. However, it has a first damper unit, a second damper unit, and a coupling unit, and the coupling unit couples the first damper unit to the second damper unit so that torque is transmitted. However, it has been found that the turbine wheel can be provided by being coupled to the coupling unit so that torque is transmitted.

As a result, the effective (rotational) mass of the coupling unit between the first damper unit and the second damper unit is increased, so that the damper characteristics of the torque transmission device of the series damper can be easily changed. it can.

In another embodiment, the torque transmitter comprises at least one Tuned Mass Damper, particularly a centrifugal pendulum, and the Tuned Mass Damper has at least one Tuned Mass Damper Flank. , Tuned mass damper flanges are coupled to the coupling unit so that torque is transmitted, preferably shape-coupled and / or force-coupled, or in one piece and of the same material as the coupling unit. Is formed of.

In another embodiment, the Tuned Mass Damper Flange has an internal dentition and the Tuned Mass Damper Flange is axially located between the first coupling portion and the second coupling portion. This internal dentition engages within the aforementioned external dentition and couples the Tuned Mass Damper flange to the coupling hub so that torque is transmitted.

In another embodiment, the rotation speed adaptive type dynamic damper is located between the first damper unit and the second damper unit in the radial direction and / or preferably the first. The damper unit, the second damper unit, and the rotation speed adaptive type dynamic vibration absorber are arranged so as to have an overlap in the axial direction. As a result, the torque transmission device can be formed particularly compactly.

In another embodiment, the first damper unit has a first damper element having a first rigidity, and the second damper unit has a second damper element having a second rigidity. The tensioning means has a third stiffness, the third stiffness being greater than the first stiffness and / or the second stiffness.

In another embodiment, the coupling unit has another coupling portion, the other coupling portion being coupled to the turbine wheel on one side and the first coupling portion on the other side. And / or coupled to a second coupling portion, preferably another coupling portion is a first coupling portion and / or a second cup by a shape coupling, particularly an axially insertable coupling. It is connected to the ring part.

In another embodiment, the torque transmitter comprises another speed-adaptive dynamic vibration absorber with a dynamic vibration absorber flange, and the other coupling portion described above extends substantially axially. This other dynamic vibration absorber flange extends substantially in the radial direction and is coupled to the other coupling portion described above radially inside or outside by an axially insertable coupling.

Hereinafter, the present invention will be described in detail with reference to the drawings.

It is the schematic of the torque transmission device by 1st Embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the embodiment shown in FIG. It is a half-divided vertical sectional view of the torque transmission device according to the second embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the third embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to 4th Embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the fifth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the sixth embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to 7th Embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the eighth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to a ninth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the tenth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the eleventh embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to a twelfth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the thirteenth embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to the fourteenth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the fifteenth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the sixteenth embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the 17th embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the eighteenth embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to 19th Embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the twentieth embodiment. It is a half-division vertical cross-sectional view of the torque transmission device according to 21st Embodiment. It is a half-divided vertical sectional view of the torque transmission device according to the 22nd embodiment.

FIG. 1 shows a schematic view of the torque transmission device 10 according to the first embodiment. The torque transmission device 10 includes an input side 20 and an output side 25. The input side 20 can be connected to, for example, a drive motor of a power train of an automobile so that torque can be transmitted. The output side 25 can be connected to, for example, a transmission 30, particularly a vehicle transmission of an automobile, so that torque can be transmitted. The output side 25 may be connected to other components of the power train so that torque can be transmitted. The input side 20 and the output side 25 may be reversed.

Further, the torque transmission device 10 includes a hydrodynamic converter 35 utilizing the mechanical action of the fluid, a lockup clutch 40, a series damper 45, and a first to fourth rotation speed adaptive type dynamic vibration absorber 50. , 55, 60, 65 and so on.

The rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 are formed as a centrifugal pendulum as an example. The rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 may be formed in different forms. In particular, the rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 are trapezoidal having one or more dynamic vibration absorber mass bodies 220, 235, 245, 255, 325 arranged so as to be located inside or outside. It may be formed as a centrifugal pendulum or a parallel centrifugal pendulum. At that time, the number of rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 in this embodiment is an example. It is self-evident that a different number of rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 may be provided. The arrangement of the rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 is also an example, and may be selected in a different form. Individual or all speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 may be omitted.

The series damper 45 has at least one first damper unit 70, a second damper unit 75, and a coupling unit 80. The first damper unit 70 has a first damper element 85, and the second damper unit 75 has a second damper element 90. The damper elements 85, 90 may be an assembly consisting of one or more springs, in particular compression springs, tension springs and / or arc springs. Other configurations of damper elements 85, 90 are also possible.

The first damper unit 70 has a first damper input side 95 and a first damper output side 100. The second damper unit 75 has a second damper input side 105 and a second damper output side 110. The first damper element 85 connects the first damper input side 95 to the first damper output side 100. At that time, for torque transmission, the first damper input side 95 can rotate about the rotation axis 15 (shown in FIG. 2) with respect to the first damper output side 100, and the first damper element 85. Can be compressed, for example, in the circumferential direction.

The coupling unit 80 is arranged between the first damper output side 100 and the second damper input side 105, and preferably the first damper output side 100 is on the second damper input side 105. It is rigidly connected. The second damper element 90 connects the second damper input side 105 to the second damper output side 110 so that torque is transmitted. At that time, for torque transmission, the second damper input side 105 is rotatable about the rotation axis 15 (shown in FIG. 2) with respect to the second damper output side 110, and the second damper element 90. Can be compressed, for example, in the circumferential direction. The second damper output side 110 is rigidly connected to the output side 25.

The hydrodynamic converter 35 includes a pump wheel 115, a turbine wheel 120, and a converter liquid (not shown). The pump wheel 115 is connected to the turbine wheel 120 during the operation of the torque transmission device 10 due to the mechanical effect of the fluid. However, the number of revolutions is different between the pump wheel 115 and the turbine wheel 120. The pump wheel 115 is connected to the input side 20 so that torque can be transmitted.

The lockup clutch 40 is arranged in parallel with the hydrodynamic converter 35. The clutch input side 125 of the lockup clutch 40 is connected to the input side 20, and the clutch output side 130 of the lockup clutch 40 is connected to the first damper input side 95.

The first rotation speed adaptive type dynamic vibration absorber 50 is attached to the coupling unit 80. Further, the coupling unit 80 is connected to the turbine wheel 120 so that torque can be transmitted. A second rotation speed adaptive type dynamic vibration absorber 55 is further arranged on the turbine wheel 120. The third rotation speed adaptive type dynamic vibration absorber 60 is arranged on the first damper output side 100, and the fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged on the second damper input side 105. There is.

This implementation is performed when the lockup clutch 40 is closed, that is, when the clutch input side 125 is connected to the clutch output side 130 so that torque is transmitted by frictional coupling in the lockup clutch 40. In the embodiment, as an example, the torque coming from the input side 20 is guided to the first damper input side 95 via the lockup clutch 40. The output side 25 provides a counter torque to the torque to be transmitted. The first damper input side 95 tensions the first damper element 85 with respect to the first damper output side 100. Further, the torque to be transmitted is transmitted to the second damper unit 75 via the coupling unit 80. The second damper input side 105 tensions the second damper element 90 with respect to the second damper output side 110.

When the torque to be transmitted has rotational unevenness, for example, torsional vibration, the rotational unevenness is reduced by the spring elastic motion of the damper elements 85 and 90. Further, the rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 are excited to absorb rotation unevenness at least partially, and as a result, a particularly smooth torque is provided to the output side 25.

FIG. 2 shows a half-divided vertical cross-sectional view of the torque transmission device 10 schematically shown in FIG. However, the illustration of the pump wheel 115 is omitted.

In the present embodiment, the lockup clutch 40 is formed as a multi-plate clutch as an example. At that time, the clutch output side 130 is connected to the first damper input unit 135 forming the first damper input side 95.

The first damper input side 95 has a first damper input unit 135. The first damper input unit 135 is connected to the clutch output side 130 on the inner side in the radial direction. The first damper input portion 135 is connected to the first end surface of the first damper element 85 on the outer side in the radial direction. The first damper output side 100 has a first damper output unit 145 and a second damper output unit 150. The first damper output unit 145 and the second damper output unit 150 are arranged at intervals in the axial direction, and the first damper output unit 145 and the second damper output unit 150 are arranged in the axial direction. A first damper input portion 135 is engaged with the 150. The first damper output unit 145 and the second damper output unit 150 are coupled to each other, for example, riveted, screwed or bonded to each other. The first damper output side 100 is connected to the second end surface of the first damper element 85. As a further example, the first damper output side 100 positions the first damper element 85.

When the torque is transmitted from the input side 20 to the output side 25, the torque is introduced from the first damper input unit 135 to the first damper element 85 via the first end face, and the first damper element 85 is introduced. It is introduced into the first and second damper output units 145 and 150 via the end face of 2.

The output side 25 may have, for example, a driven shaft 155, and the driven shaft 155 may be formed as a transmission input shaft of the transmission 30. The driven shaft 155 has a first section 160 and a second section 165, and the second section 165 is arranged adjacent to the first section 160 in the axial direction as an example in the present embodiment. ing. As an example, the peripheral surface of the second section 165 has the first external dentition 166, while the peripheral surface of the first section 160, for example, has a sliding surface on the outer surface.

The coupling unit 80 has a first coupling portion 170, at least one second coupling portion 175, and a coupling hub 176. The first coupling portion 170 and / or the second coupling portion 175 is formed in a disk shape and is connected to the second damper output portion 150 on the outer side in the radial direction. At that time, the first coupling portion 170 and the second damper output portion 150 may be formed in one piece and made of the same material. The first coupling portion 170 has a first internal dentition 180, and the second coupling portion 175 has a second internal dentition 185. The first internal dentition 180 and the second internal dentition 185 are formed in the same manner as an example.

The coupling hub 176 is rotatably arranged in the first section 160 of the driven shaft 155 inside in the radial direction. The coupling hub 176 has a second external dentition 190, the second external dentition 190 being formed to correspond to a first internal dentition 180 and a second internal dentition 185. Within the second external dentition 190, the first internal dentition 180 and the second internal dentition 185 are engaged. As a result, the coupling hub 176 connects the first coupling portion 170 to the second coupling portion 175. Additionally, means not shown may be provided to axially position the coupling hub 176 and the first and / or second coupling portions 170,175.

The first damper unit 70 is arranged adjacent to the lockup clutch 40 in the axial direction. The second damper unit 75 is arranged between the turbine wheel 120 and the first damper unit 70 in the axial direction. The second damper input side 105 has a second damper input unit 195 and a third damper input unit 200 arranged at intervals with respect to the second damper input unit 195 in the axial direction. There is. The second and third damper input units 195 and 200 are coupled to each other. At that time, the third damper input unit 200 is arranged on the side opposite to the first damper unit 70, and is connected to the turbine wheel 120 on the inner side in the radial direction. The second coupling portion 175 is connected to the second damper input portion 195 on the outer side in the radial direction. In the present embodiment, as an example, the second coupling portion 175 and the second damper input portion 195 are formed in one piece and made of the same material. It is self-evident that the second damper input section 195 and the second coupling section 175 may be formed of a plurality of parts, and in this configuration, the second damper with respect to the configuration shown in FIG. The input portion 195 is coupled to the inside in the radial direction and the outer side in the radial direction of the second coupling portion 175. The second and third damper input units 195, 200 are connected to the first end face of the second damper element 90.

The second damper output side 110 has a third damper output unit 205 between the second damper input unit 195 and the third damper input unit 200. The third damper output unit 205 is connected to the second end face of the second damper element 90 on the outer side in the radial direction. The third damper output unit 205 has a third internal dentition 210 inside in the radial direction, and the third internal dentition 210 is formed so as to correspond to the first external dentition 166 of the driven shaft 155. And engage within the first external dentition 166.

The first rotation speed adaptive type dynamic vibration absorber 50 has a first dynamic vibration absorber flange 215 and a first dynamic vibration absorber mass body 220. In the present embodiment, since the first rotation speed adaptive type dynamic vibration absorber 50 is formed as a centrifugal pendulum located on the outside, the first dynamic vibration absorber mass body 220 is a first dynamic vibration absorber flange. It is located on both sides of the 215. Further, the first rotation speed adaptive type dynamic vibration absorber 50 has a guide device (not shown), and the guide device causes the first dynamic vibration absorber mass body 220 to be attached to the first dynamic vibration absorber flange 215. It is connected. When the rotational unevenness is introduced into the first Tuned Mass Damper Flange 215, the first Tuned Mass Dammer 220 is guided by the first guide device along the first Tuned Mass Damper Trajectory. The first Tuned Mass Damper Flange 215 is arranged axially between the first and second coupling portions 170 and 175 and between the damper units 70 and 75.

In this embodiment, the first Tuned Mass Damper Flange 215 has a fourth internal dentition 225 as an example. The fourth internal dentition 225 is formed to correspond to the second external dentition 190 of the coupling hub 176 and engages in the second external dentition 190, so that the first dynamic vibration absorber The flange 215 is also connected to the coupling hub 176 so that torque can be transmitted, and thus to the first coupling portion 170 and the second coupling portion 175. The first Tuned Mass Damper 220 is arranged radially outward with respect to the first damper unit 70 and the second damper unit 75.

The second rotation speed adaptive type dynamic vibration absorber 55 has a second dynamic vibration absorber flange 230 and a second dynamic vibration absorber mass body 235, and the second dynamic vibration absorber mass body 235 has a second dynamic vibration absorber mass body 235. It is connected to the second tuned mass damper flange 230 by the guide device (not shown) of 2, and when the rotation unevenness is introduced into the second dynamic vibration absorber flange 230, the second vibration absorber to absorb the rotation unevenness. Guided along the trajectory of the second Tuned Mass Damper. The second Tuned Mass Damper Flange 230 is coupled to the Turbine Wheel 120 on the inside in the radial direction. At that time, the second vibration absorber flange 230 is arranged between the turbine wheel 120 and the second damper unit 75 in the axial direction.

The third rotation speed adaptive type dynamic vibration absorber 60 is arranged so as to have an overlap (overlap) with the first damper unit 70 in the axial direction and on the side closer to the lockup clutch 40 in the axial direction. .. The third rotation speed adaptive type dynamic vibration absorber 60 is arranged on the outer side in the radial direction of the first damper unit 70, and is formed similar to the first rotation speed adaptive type dynamic vibration absorber 50. , Has a third Tuned Mass Damper Flange 240 and a Third Tuned Mass Dammer 245. The third vibration absorber mass body 245 is connected to the third dynamic vibration absorber flange 240 by a third guide device (not shown), and when rotation unevenness is introduced into the third dynamic vibration absorber flange 240, Guided along a third Tuned Mass Damper trajectory. In the present embodiment, the third vibration absorber flange 240 is connected to the second damper output unit 150 on the inner side in the radial direction as an example. In the present embodiment, as an example, the second damper output unit 150, the first coupling unit 170, and the third tuned mass damper flange 240 are formed in one piece and made of the same material, for example, in a disk shape. Has been done. It is self-evident that other configurations are possible.

The fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged between the first and second rotation speed adaptive type dynamic vibration absorbers 50 and 55 in the axial direction and outside the radial direction of the series damper 45. It has a fourth Tuned Mass Damper Flange 250 and a fourth Tuned Mass Dammer 255. The fourth Tuned Mass Damper 255 is connected to the Fourth Tuned Mass Damper Flange 250 by a fourth guide device (not shown). When rotational unevenness is introduced into the fourth Tuned Mass Damper Flange 250, the fourth Tuned Mass Dammer 255 is guided along the fourth Tuned Mass Damper Trajectory by the fourth guide device, at which time. Absorbs rotational unevenness at least partially. In this embodiment, the fourth vibration absorber flange 250 is connected to the second damper input unit 195 on the inner side in the radial direction. As an example, as shown in FIG. 2, the second coupling portion 175, the second damper input portion 195, and the fourth vibration absorber flange 250 are made of the same material in one piece, and are shown as an example. It may be formed in a disk shape as shown in 2. In this embodiment, all rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 are at the same level radially outward and radially with respect to the first damper unit 70 and the second damper unit 75. Have been placed. It is self-evident that different arrangements of rotation speed adaptive dynamic absorbers 50, 55, 60, 65 are possible.

When the torque from the input side 20 to the output side 25 is introduced, the first damper element 85 is subjected to the circumferential direction by the first damper input unit 135 and the first and second damper output units 145 and 150. The torque is then transmitted between the first damper input side 95 and the first damper output side 100. The torque is then transmitted from the second damper output section 150 to the first coupling section 170, and the first coupling section 170 itself transfers the torque to the coupling hub 176 via the first internal dentition 180. Introduce. Rotational unevenness is also guided through the coupling hub 176 to the first Tuned Mass Damper Flange 215, which is not present in the direct torque flow. Torque passes through the first Tuned Mass Damper flange 215 and is introduced into the second coupling portion 175. The second coupling unit 175 further transmits torque to the second damper input unit 195, and the second damper input unit 195 and the third damper input unit 200 transmit the second damper element 90 in the circumferential direction. Make me nervous. Due to this tension, the second damper element 90 delivers torque to the third damper output unit 205, and the third damper output unit 205 itself transfers torque to the driven shaft 155 via the third internal dentition 210. Introduce.

Since the turbine wheel 120 is connected to the coupling unit 80, when the lockup clutch 40 is released, the rotation unevenness becomes the rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65, and so on. It is further guaranteed that the damper unit 75 of 2 absorbs vibration. That is, torque is introduced from the turbine wheel 120 through the third damper input 200 to the second damper input 195, and from the third damper input 200 and the second damper input 195. This is because the second damper element 90 is introduced into the second damper element 90, and the second damper element 90 is strained by this torque against the counter torque applied to the driven shaft 155. Torque is introduced into the driven shaft 155 in the second section 165 via the second damper element 90 to the third damper output unit 205 and the third internal dentition 210. Since the turbine wheel 120 is coupled to the coupling unit 80, the effective mass on the input side of the second damper unit 75 is increased, so that the total weight of the torque transmission device 10 is light and torque. The transmission device 10 exhibits advantageous dynamic vibration absorber characteristics.

FIG. 3 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the second embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 shown in FIGS. 1 and 2. Unlike the torque transmission device 10 shown in FIGS. 1 and 2, the coupling unit 80 additionally has a third coupling portion 260 and a fourth coupling portion 265. The third coupling portion 260 has a fifth internal dentition 270, and the fifth internal dentition 270 is formed to correspond to a second external dentition 190 of the coupling hub 176. Since the fifth internal dentition 270 engages within the second external dentition 190, the third coupling portion 260 is connected to the coupling hub 176 so that torque is transmitted. The third coupling portion 260 is arranged between the first dynamic vibration absorber flange 215 and the second damper input portion 195 in the axial direction, and is formed in a disk shape.

The third coupling portion 260 is coupled to the fourth coupling portion 265 on the outer side in the radial direction by the first insertion coupling portion 280. Since the first insertion coupling portion 280 can be eliminated by the axial movement, the fourth coupling portion 265 can be easily disassembled from the third coupling portion 260 by the axial insertion movement, or again. It can be assembled. For example, for this purpose, the fourth coupling portion 265 may have a finger portion extending in the axial direction, and the finger portion may correspond to the radial outer side of the third coupling portion 260, respectively. The third coupling portion 260 is connected to the fourth coupling portion 265 so that it engages in the provided receiving portion and thus the torque is transmitted. In the present embodiment, the third coupling portion 260 is formed in a disk shape as an example, while the fourth coupling portion 265 extends substantially in the axial direction and is formed in a ring shape, for example. You may be. Further, the fourth coupling portion 265 is arranged on the outer side in the radial direction of the second damper unit 75 and on the inner side in the radial direction of the rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65. The fourth coupling portion 265 is coupled to the turbine wheel 120 behind the first plug-in coupling portion 280 when viewed axially. In the present embodiment, the fourth coupling portion 265 is additionally coupled to the fourth dynamic vibration absorber flange 250 of the fourth rotation speed adaptive type dynamic vibration absorber 65 by the second insertion coupling portion 285. ing. The second plug-in coupling portion 285 is formed so as to be able to be coupled or disengaged in the axial direction. Thereby, during assembly, for example, when the turbine wheel 120 is inserted into the torque transmission device 10, the connection in which the torque is transmitted is connected between the third coupling portion 260 and the fourth coupling portion 265. However, it can be easily guaranteed between the fourth coupling portion 265 and the fourth vibration absorber flange 250.

For example, the second plug-in joint 285 may be formed by the tongue piece of the fourth coupling portion 265. The tongue piece extends axially in part and engages in a corresponding notch provided in the fourth Tuned Mass Damper Flange 250.

FIG. 4 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the third embodiment. The torque transmission device 10 is formed substantially the same as the configuration shown in FIG. Unlike the configuration shown in FIG. 3, the second rotation speed adaptive type dynamic vibration absorber 55 is coupled to the turbine wheel 120 by a third plug-in coupling portion 290 that can be coupled or disengaged in the axial direction. At that time, the third plug-in joint portion 290 may be formed substantially the same as the first and second plug-in joint portions 280 and 285 described with reference to FIG.

In addition to the second embodiment shown in FIG. 3, the torque transmission device 10 includes a first tensioning means 295 and a second tensioning means 300. At that time, the first tensioning means 295 is arranged between the first coupling portion 170 and the first Tuned Mass Damper Flange 215 in the circumferential direction, and the first Tuned Mass Damper Flange 215 is placed in the first position. Tension the coupling portion 170 of 1 in the circumferential direction. This guarantees the avoidance of dentition noise when the first internal dentition 180 and the fourth internal dentition 225 engage the second external dentition 190.

The second tensioning means 300 tensions the third coupling portion 260 against the first Tuned Mass Damper Flange 215. At this time, in the present embodiment, as an example, the second tensioning means 300 is arranged on the outer side in the radial direction of the first tensioning means 295 and on the inner side in the radial direction of the damper units 70 and 75. The first and second tensioning means 295,300 may be, for example, an arc-shaped spring extending in the circumferential direction or a compression spring arranged in the tangential direction with respect to the circular orbit about the rotation axis 15.

FIG. 5 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the fourth embodiment. The torque transmission device 10 is formed substantially the same as the configuration shown in FIGS. 1 to 4, particularly the configuration shown in FIG. Unlike the configuration shown in FIG. 4, the second tensioning means 300 shown in FIG. 4 is omitted. Additionally, the coupling unit 80 has a support element 305, the support element 305 has a seventh internal dentition 310, and the seventh internal dentition 310 is in the second external dentition 190. Engage. The support element 305 extends radially and is formed substantially in a disk shape. The first tensioning means 295 is arranged between the support element 305 and the first coupling portion 170, and tensions the first coupling portion 170 with respect to the support element 305 in the circumferential direction. The support element 305 is arranged axially on the outermost side of the coupling hub 176 on the side closer to the lockup clutch 40.

FIG. 6 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the fifth embodiment. The torque transmission device 10 is substantially a combination of the configuration of the torque transmission device 10 shown in FIG. 2 and the configuration of the torque transmission device 10 shown in FIGS. 4 and 5. Unlike this combination, the second plug-in coupling portion 285 and the third coupling portion 260 are omitted. The fourth coupling portion 265 is coupled to the third damper output portion 205 by the first insertion coupling portion 280. In the present embodiment, as an example, the first insertion / coupling portion 280 is arranged on the outer side in the radial direction of the second damper unit 75. Further, the turbine wheel 120 is rotatably supported by the driven shaft 155 by the turbine flange 311. The turbine flange 311 is arranged inside the turbine wheel 120 in the radial direction.

FIG. 7 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the sixth embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 shown in FIG. Unlike the torque transmission device 10 shown in FIG. 6, the first plug-in coupling portion 280 is formed between the fourth coupling portion 265 and the second damper input portion 195, so that the fourth plug-in coupling portion 280 is formed. The coupling portion 265 engages in the second damper input portion 195 on the radial outer side of the second damper element 90. If the 4th Tuned Mass Damper Flange 250 is one piece with the 2nd Damper Input Section 195 and is made of the same material, the 4th Coupling Section 265 will be the 4th Tuned Mass Damper Flange 250. May engage in.

FIG. 8 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the seventh embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 described with reference to FIG. 7. Unlike the torque transmission device 10 described with reference to FIG. 7, the torque transmission device 10 includes a fifth rotation speed adaptive type dynamic vibration absorber 315. The fifth rotation speed adaptive type dynamic vibration absorber 315 has a fifth dynamic vibration absorber flange 320 and at least one fifth dynamic vibration absorber mass body 325. The fifth Tuned Mass Damper 325 is coupled to the fifth Tuned Mass Damper Flange 320 by a fifth guide device (not shown). When the rotational unevenness is introduced into the fifth Tuned Mass Damper Flange 320, the fifth Tuned Mass Dammer 325 is guided along the fifth Tuned Mass Damper Trajectory by the fifth guide device. The fifth Tuned Mass Damper 325 absorbs rotational unevenness at least partially by a pendulum motion along the fifth Tuned Mass Damper trajectory. The fifth Tuned Mass Damper Flange 320 extends radially and is connected to the fourth coupling portion 265 inside the radial direction. At that time, the fifth rotation speed adaptive type dynamic vibration absorber 315 includes the second damper unit 75 in the radial direction and the first to fourth rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65. It is placed between. The fifth rotation speed adaptive type dynamic vibration absorber 315 is arranged between the turbine wheel 120 and the fourth dynamic vibration absorber flange 250 in the axial direction.

FIG. 9 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the eighth embodiment. The torque transmission device 10 is substantially a combination of the torque transmission devices 10 described with reference to FIGS. 2 and 6. Unlike this combination, the coupling hub 176 is omitted. Further, by omitting the coupling hub 176, the first section 160 of the driven shaft 155 can also be omitted.

As a result, the second section 165 of the driven shaft 155 is directly adjacent to the region where the turbine wheel 120 is rotatably supported by the driven shaft 155 with respect to the driven shaft 155.

Further, since the first coupling portion 170 and the second coupling portion 175 are shortened inward in the radial direction, the first coupling portion 170 and the second coupling portion 175 are shortened in the radial direction. , Are arranged at intervals from the driven shaft 155. An additional first tensioning means 295 is provided, the first tensioning means 295 tensioning the first coupling portion 170 against the second coupling portion 175. Additionally, the fourth Tuned Mass Damper Flange 250 is engageable within the first tensioning means 295.

The first damper element 85 has the first rigidity. The second damper element 90 has a second rigidity. The first tensioning means 295 has a third stiffness, the third stiffness being greater than the first stiffness and / or the second stiffness. It is particularly advantageous if the third stiffness is at least twice, preferably five times, the first stiffness and / or the second stiffness. However, it is desirable that the third stiffness be at least 100 times smaller than the first stiffness and / or the second stiffness.

FIG. 10 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the ninth embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 shown in FIG. Unlike the torque transmission device 10 shown in FIG. 9, the first rotation speed adaptive type dynamic vibration absorber 50 is omitted. Further, the first tensioning means 295 has a disc spring or a leaf spring, and the disc spring or the leaf spring transmits torque from the first coupling portion 170 to the second coupling portion 175 in the circumferential direction. Especially rigid as it is done. This can ensure that the first tensioning means 295 exhibits a particularly rigid, but at the same time, (weak) spring elasticity in the circumferential direction.

FIG. 11 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the tenth embodiment. The torque transmission device 10 is substantially a combination of the torque transmission devices 10 shown in FIGS. 9 and 10. At that time, the first tensioning means 295 is formed as an arc-shaped spring or a compression spring as described with reference to FIG. 9, and the first coupling portion 170 is tensioned in the circumferential direction by the second coupling portion 175. And has the third rigidity described in FIGS. 9 and 10.

FIG. 12 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the eleventh embodiment. The torque transmission device 10 is formed substantially the same as the configuration shown in FIGS. 9 to 11. Unlike the configurations shown in FIGS. 9 to 11, the second coupling portion 175 is omitted. The first coupling portion 170 is formed in an isolated shape as seen in the half-divided vertical cross-sectional view shown in FIG. At one end of the first coupling portion 170, which is arranged on the opposite side of the second damper output portion 150, the first coupling portion 170 is subjected to the second damper input by the second insertion coupling portion 285. It is coupled to the portion 195 or the fourth vibration absorber flange 250 so that torque is transmitted. At that time, since the first coupling portion 170 engages in the fourth dynamic vibration absorber flange 250 or the second damper input portion 195 at the free end, the axial assembly direction of the torque transmission device 10 and the assembling direction and / Or the disassembly direction is guaranteed.

In FIG. 12, a second plug-in coupling portion 285 is arranged radially outside the second damper unit 75 between the fourth Tuned Mass Damper 255 and the second damper unit 75. .. Further, in the present embodiment, as an example, the fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged inside the first rotation speed adaptive type dynamic vibration absorber 50 in the radial direction. As a further example, the first vibration absorber flange 215 is arranged on one piece of the third damper input portion 200 and on the outer side in the radial direction of the third damper input portion 200 with the same material. It is self-evident that the third damper input section 200 and the first Tuned Mass Damper Flange 215 may be formed from a plurality of parts.

FIG. 13 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the twelfth embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 described with reference to FIG. Unlike the torque transmission device 10 described with reference to FIG. 12, the second insertion / coupling portion 285 is arranged inside the second damper unit 75 in the radial direction. As a result, the first coupling portion 170 can be formed to be longer in the axial direction and have a smaller curvature than that in FIG.

FIG. 14 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the thirteenth embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 described with reference to FIG. Unlike the torque transmission device 10 described with reference to FIG. 12, the first rotation speed adaptive type dynamic vibration absorber 50 that depends on the rotation speed is omitted. Further, the first damper unit 70 has a first damper input unit 135 and a second damper input unit 195, and has a first damper input unit 135 and a second damper input unit 195 in the axial direction. A first damper output unit 145 is arranged between the two. The first damper input unit 135 and the second damper input unit 195 are coupled to each other. The first coupling portion 170 is coupled to the third damper input portion 200 or the fourth vibration absorber flange 250 by the second insertion coupling portion 285. At that time, in the present embodiment, the first coupling portion 170 is inserted into the fourth damper flange 250 and / or the third damper input portion 200 on the left side, that is, the side closer to the lockup clutch 40. Is done.

The second damper unit 75 has a second damper output unit 150 and a third damper output unit 205, and the second damper output unit 150 and the third damper output unit 205 are coupled to each other. A third damper input unit 200 is engaged between the second damper output unit 150 and the third damper output unit 205 in the axial direction. Both the second damper output unit 150 and the third damper output unit 205 are internally engaged in the first external dentition 166 of the driven shaft 155 in order to introduce torque to the driven shaft 155.

The turbine wheel 120 is coupled by a second plug-in coupling portion 285 to a fourth vibration absorber flange 250 and / or a third damper input portion 200 so that torque is transmitted. At that time, the engagement of the fourth coupling portion 265 is with the side of the fourth vibration absorber flange 250 opposite to the first coupling portion 170, that is, the side closer to the turbine wheel 120 or the lockup clutch 40. Is done on the other side.

FIG. 15 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the fourteenth embodiment. The torque transmission device 10 is formed substantially the same as the configuration of the torque transmission device 10 described with reference to FIG. Unlike the configuration of the torque transmission device 10 described with reference to FIG. 14, the plug-in coupling portions 280, 285, and 290 are omitted. Further, with respect to the configuration shown in FIG. 14, the fourth coupling portion 265 is formed longer in the axial direction than that shown in FIG. At that time, a fourth tuned mass damper flange 250 is attached to the outer side of the fourth coupling portion 265 in the radial direction, and a third damper input portion 200 is attached to the inner side in the radial direction.

The first coupling portion 170 extends from the outer side in the radial direction to the inner side in the radial direction with respect to the first damper unit 70, and is coupled to the fourth coupling portion 265. Further, the fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged between the first damper unit 70 and the second damper unit 75 in the radial direction.

FIG. 16 shows the torque transmission device 10 according to the fifteenth embodiment. The torque transmission device 10 is substantially the same as the embodiment of the torque transmission device 10 shown in FIG. However, unlike the embodiment of the torque transmission device 10 shown in FIG. 15, the configuration of the torque transmission device 10 shown in FIG. 16 is formed to be slimmer in the axial direction than the torque transmission device 10 shown in FIG.

FIG. 17 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the sixteenth embodiment. The torque transmission device 10 is substantially a combination of the configurations of the torque transmission device 10 described with reference to FIGS. 14 and 15. Unlike this combination, the fourth rotation speed adaptive type dynamic damper 65 is omitted. Further, the first coupling portion 170 is formed in a disk shape, and is arranged in the radial inner side of the second tuned mass damper flange 230 and, for example, the second tuned mass damper flange 230. It is formed in one piece and made of the same material together with the damper output portion 145 of the above and the third damper input portion 200 arranged inside the first coupling portion 170 in the radial direction. The first coupling portion 170 is coupled to the fourth coupling portion 265 by the first insertion coupling portion 280 and is coupled to the turbine wheel 120 via the fourth coupling portion 265.

FIG. 18 shows the torque transmission device 10 according to the 17th embodiment. The torque transmission device 10 is substantially a combination of the torque transmission device 10 shown in FIG. 15 and the torque transmission device 10 shown in FIG. At that time, the configuration is substantially the same as the configuration shown in FIG. 15, but the first coupling unit 170, the first damper output unit 145, the third dynamic vibration absorber flange 240, and the third damper input A one-piece, same-material configuration of part 200 is incorporated into the configuration shown in FIG. Further, with respect to FIG. 17, the second plug-in joint portion 285 and the third plug-in joint portion 290 are omitted. Further, the fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged inside the second rotation speed adaptive type dynamic vibration absorber 55 in the radial direction and is attached to the turbine wheel 120.

FIG. 19 shows the torque transmission device 10 according to the eighteenth embodiment. The torque transmission device 10 is formed substantially the same as the configuration shown in FIG. Unlike the configuration shown in FIG. 18, a first rotation speed adaptive type dynamic vibration absorber 50 is additionally provided with respect to FIG. 18, and the first dynamic vibration absorber flange 215 and the first coupling are provided. The unit 170 is summarized. That is, the first Tuned Mass Damper 220 is attached to the first coupling portion 170. As a result, the second rotation speed adaptive type dynamic vibration absorber 55 is arranged at the level of the fourth rotation speed adaptive type dynamic vibration absorber 65 in the radial direction. Further, the first rotation speed adaptive type dynamic vibration absorber 50 is arranged between the first damper unit 70 and the second damper unit 75 in the radial direction. When viewed in the axial direction, the first rotation speed adaptive type dynamic vibration absorber 50, the third rotation speed adaptive type dynamic vibration absorber 60, and the first and second damper units 70 and 75 are in the axial direction. It is arranged so as to have an overlap. At that time, having at least two components overlapping in the axial direction means that, in the present embodiment, as an example, the first and third rotation speed adaptive type dynamic vibration absorbers 50 and 60, and the first and second dampers. When the units 70 and 75 are projected along the one rotation plane with respect to the rotation axis 15 in the projective plane arranged so as to include the rotation axis 15, these components are superimposed in this projection plane. Will be done.

FIG. 20 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the nineteenth embodiment. The torque transmission device 10 is formed substantially the same as the configuration of the torque transmission device 10 shown in FIG. Unlike the configuration of the torque transmission device 10 shown in FIG. 12, the second damper output unit 150, the first coupling unit 170, and the second damper input unit 195 are made of the same material in one piece. The first coupling portion 170 is formed and extends diagonally with respect to the rotation axis 15, while the second damper output portion 150 and the second damper input portion 195 are different from each other. It extends in the plane of rotation. Further, the first rotation speed adaptive type dynamic vibration absorber 50 and the fourth rotation speed adaptive type dynamic vibration absorber 65 are omitted, and as a result, the torque transmission device 10 exclusively adjusts to the second rotation speed. It includes a type dynamic vibration absorber 55 and a third rotation speed adaptive type dynamic vibration absorber 60.

FIG. 21 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the twentieth embodiment. The torque transmission device 10 is formed substantially the same as the torque transmission device 10 in FIG. In addition, a fourth rotation speed adaptive type dynamic vibration absorber 65 is provided, and the fourth dynamic vibration absorber flange 250 is coupled to the third damper input portion 200 on the inner side in the radial direction. In the present embodiment, the fourth vibration absorber flange 250 and the third damper input portion 200 are formed in one piece and made of the same material.

Further, when viewed in the radial direction, the fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged inside the second rotation speed adaptive type dynamic vibration absorber 55 in the radial direction. The second rotation speed adaptive type dynamic vibration absorber 55 is arranged more inward in the radial direction than the third rotation speed adaptive type dynamic vibration absorber 60. The fourth rotation speed adaptive type dynamic vibration absorber 65 is arranged between the second rotation speed adaptive type dynamic vibration absorber 55 and the third rotation speed adaptive type dynamic vibration absorber 60 in the axial direction. There is. The turbine wheel 120 is coupled to the third damper input 200 on the inner radial side (eg, as in FIGS. 9, 10, 11, 12 and 13).

FIG. 22 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the 21st embodiment.

The torque transmission device 10 is formed substantially the same as the configuration of the torque transmission device 10 shown in FIG. Unlike the configuration of the torque transmission device 10 shown in FIG. 21, the fourth rotation speed adaptive type dynamic vibration absorber 65 is omitted. Further, the first coupling portion 170 is coupled to the fourth coupling portion 265. As a result, the turbine wheel 120 is coupled to the first coupling portion 170 via the fourth coupling portion 265. The arrangement of the coupling portion between the first coupling portion 170 and the fourth coupling portion 265 substantially corresponds to the configuration described with reference to FIG. At that time, the second plug-in joint portion 285 may be provided as described with reference to FIG. However, in FIG. 22, the second plug-in coupling portion 285 is omitted, and as a result, the first coupling portion 170 is firmly coupled to the fourth coupling portion 265.

FIG. 23 shows a half-divided vertical cross-sectional view of the torque transmission device 10 according to the 22nd embodiment. The torque transmission device 10 is formed substantially the same as the configuration described with reference to FIG. Unlike the configuration described with reference to FIG. 22, a fourth rotation speed adaptive type dynamic vibration absorber 65 is provided, and the fourth dynamic vibration absorber flange 250 is arranged on the outer side in the radial direction of the second damper unit 75. It is connected to the third damper input unit 200 at one end on the inner side in the radial direction.

The configuration shown in FIGS. 1 to 23 guarantees a modular structure of the torque transmission device 10. This allows, in particular, to incorporate components as needed, depending on the components that one wants to combine from time to time, especially the first to fourth speed-adaptive Tuned Mass Dampers 50, 55, 60, 65 and damper units 70, 75. , A unit system that can be omitted can be provided. At that time, in the present embodiment, the first damper unit 70 is independently designed regardless of the second damper unit 75, and as a result, both damper units 70 and 75 are inside the torque transmission device 10. It is particularly advantageous to function as an individual component, whether or not it is provided in. The same applies to the speed-adaptive dynamic dampers 50, 55, 60, 65, 315 and turbine wheel 120 provided. By connecting the turbine wheel 120 to the first coupling portion 170, directly or indirectly, for example via, for example, the fourth coupling portion 265, regardless of other components, the series damper 45 and / Or the first to fourth rotation speed adaptive type dynamic vibration absorbers 50, 55, 60, 65 can be assembled in different configurations of the torque transmission device 10. Adjustments for geometric dimensioning are performed via the coupling unit 80. At that time, the hydrodynamic converter 35 may be omitted.

Further, the configuration shown in FIGS. 1 to 23, particularly the coercive force when the tensioning means 295,300 is provided, reduces or even avoids the swing of the components of the torque transmission device 10. Further, since the required tolerance can be reduced, the manufacturing cost for manufacturing the torque transmission device 10 is particularly low. In addition, the structural space is used efficiently.

10 Torque transmitter 15 Rotation axis 20 Input side 25 Output side 30 Transmission 35 Fluid dynamic converter 40 Lockup clutch 45 Series damper 50 First rotation speed adaptive type dynamic vibration absorber 55 Second rotation speed adaptive type Tuned Mass Damper 60 3rd Tuned Mass Damper 65 4th Tuned Mass Damper 70 1st Damper Unit 75 2nd Damper Unit 80 Coupling Unit 85 1st Damper Element 90 Second damper element 95 First damper input side 100 First damper output side 105 Second damper input side 110 Second damper output side 115 Pump wheel 120 Turbine wheel 125 Clutch input side 130 Clutch output side 135 First Damper input section 145 First damper output section 150 Second damper output section 155 Driven shaft 160 First section 165 Second section 166 First external tooth row 170 First coupling section 175 Second cup Ring part 176 Coupling hub 180 1st internal dentition 185 2nd internal dentition 190 2nd external dentition 195 2nd damper input part 200 3rd damper input part 205 3rd damper output part 210 3rd 215 1st Tuned Mass Damper Flange 220 1st Tuned Mass Dammer 225 4th Tuned Mass Dam 230 2nd Tuned Mass Damper Flange 235 2nd Tuned Mass Damper 240 3rd Motion Tuned Mass Damper Flank 245 Third Tuned Mass Dammer 250 4th Tuned Mass Damper Damper 255 4th Tuned Mass Dammer 260 Third Coupling 265 Fourth Coupling 270 Fifth Internal Torrow 275 6th internal dentition 280 1st plug-in joint 285 2nd plug-in joint 290 3rd plug-in joint 295 1st tensioning means 300 2nd tensioning means 305 Support element 310 7th internal dentition 311 Tuned Mass Damper 315 Fifth Tuned Mass Damper 320 Fifth Tuned Mass Damper Flange 325 Fifth Tuned Mass Dammer

Claims (9)

A torque transmission device (10) that can be rotatably supported around a rotation axis (15).
The torque transmission device (10) includes a series damper (45) having a first damper unit (70), a second damper unit (75), and a coupling unit (80).
The first damper unit (70) has a damper output side (100), and the second damper unit (75) has a damper input side (105).
The coupling unit (80) is arranged between the damper output side (100) and the damper input side (105).
In the torque transmission device (10)
The coupling unit (80) has a first coupling portion (170) and a second coupling portion (175).
The first coupling portion (170) and the second coupling portion (175) are arranged so as to be offset from each other in the axial direction.
The first coupling portion (170) couples the damper output side (100) to the second coupling portion (175).
The second coupling portion (175) couples the first coupling portion (170) to the damper input side (105) .
The torque transmission device (10) includes a driven shaft (155).
The coupling unit (80) has a coupling hub (176).
The coupling hub (176) is rotatably supported by the driven shaft (155).
The coupling hub (176) has an external dentition (190) on its peripheral surface.
The first coupling portion (170) has an internal dentition (180) and the second coupling portion (175) has another internal dentition (185).
The torque transmission device (10), characterized in that the internal dentition (180) and the other internal dentition (185) engage within the external dentition (190). Equipped with tension means (295,300)
The tensioning means (295,300) is arranged between the first component and the second component.
It said tensioning means (295,300) is formed with the first component so as to tensions with respect to the second component,
The torque transmission device (10) according to claim 1. Equipped with at least one rotation speed adaptive type dynamic vibration absorber (50, 55, 60, 65 )
The rotation speed adaptive type dynamic vibration absorber (50, 55, 60, 65) has at least one dynamic vibration absorber flange (215, 230, 240, 250, 320).
The dynamic vibration reducer flange (215,230,240,250,320) are either the torque transmission is engaged binding to said coupling unit (80) as is done, or the coupling unit and (80) 1 Formed on a piece and made of the same material,
The torque transmission device (10) according to claim 2. The Tuned Mass Damper Flange (215) has an internal dentition (225).
The Tuned Mass Damper Flange (215) is arranged between the first coupling portion (170) and the second coupling portion (175) in the axial direction.
The internal dentition (225) engages within the external dentition (190) and couples the Tuned Mass Damper Flange (215) to the coupling hub (176) so that torque is transmitted.
The torque transmission device (10) according to claim 3. The rotation speed adaptive type dynamic vibration absorber (50, 55, 60, 65) is arranged between the first damper unit (70) and the second damper unit (75) in the radial direction. Ori,
And / or a pre-Symbol first damper unit (70), wherein a second damper unit (75), the rotational speed adaptive dynamic vibration absorber and (50, 55, 60, 65), the axial Arranged to have an overlap,
The torque transmission device (10) according to claim 3 or 4. The first damper unit (70) has a first damper element (85) having a first rigidity, and the second damper unit (75) has a second damper having a second rigidity. Has element (90) and
The tensioning means (295) has a third rigidity.
The third stiffness is greater than the first stiffness and / or the second stiffness.
The torque transmission device (10) according to any one of claims 3 to 5. It comprises a hydrodynamic converter (35) turbine wheel (120) coupled to the coupling unit (80) for torque transfer.
The coupling unit (80) has another coupling portion (260,265).
The other coupling portion (260,265) is coupled to the turbine wheel (120) on one side and the first coupling portion (170) and / or the second coupling portion on the other side. The torque transmission device (10) according to claim 5 or 6, which is coupled to a coupling portion (175). Claims 5 to 7 wherein the other coupling portion (260,265) is coupled to the first coupling portion (170) and / or the second coupling portion (175) by shape coupling. The torque transmission device (10) according to any one of the above items. With another speed-adaptive dynamic damper (65) having a Tuned Mass Damper Flange (250),
The other coupling section (260,265) extends substantially axially.
The other Tuned Mass Damper Flange (250) extends substantially in the radial direction and is axially insertable into the other coupling portion (260,265) on the inside or outside of the radial direction. Combined by,
The torque transmission device (10) according to claim 7.

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